Machine tool vibration isolation system

ABSTRACT

A machine tool isolation system is disclosed. The preferred system includes a pair of platforms connected by a plurality of legs. A tool is typically connected to one platform, and a workpiece to the other. The legs are able to move one platform with respect to the other which can create vibrations. A base, typically formed by a plurality of legs, is mounted to one of the platforms to support the two platforms and legs connected therebetween. A vibration isolator is disposed between the base legs and the floor or other support on which the entire system is mounted.

BACKGROUND OF THE INVENTION

This is a continuation-in-part of the prior application having Ser. No.07/835,949 filed on Feb. 20, 1992, now U.S. Pat. No. 5,354,158. Theinvention relates to a machine for locating an operator with respect toan object, and more particularly to a versatile machine tool in whichthe tool is connected to a vibration isolation device that separates themachine tool from a support structure such as a floor.

The most versatile form of cutting tool type machine tool presently inuse is the so-called machining center which typically can accomplishmilling, drilling, boring and tapping operations in up to five axes ofmovement, the three linear orthagonal axes and two rotationaldirections. Since its introduction over thirty years ago, the machiningcenter's basic components have not changed. They typically include abed, an upright column and a spindle head carried by the column. Arotary table for holding a workpiece is typically mounted on the bed andprovides one of the rotary directions of motion. The column and tablemove relative to each other for one of the linear directions of motion,the spindle head and table move relative to each other in a verticaldirection of a second linear axis of motion, and the spindle head andworkpiece move horizontally with respect to each other for the thirdlinear direction of motion. The fifth axis is provided by rotating thespindle head or the work table in a vertical plane relative to eachother.

A sixth axis of rotary motion is available in the present machiningcenters by controlling the angular position of the spindle. The presentmachining centers may have either a horizontal spindle or a verticalspindle and they typically are controlled by computer numerical control.The machining centers usually have mechanisms for automatically changingtools from and to a magazine of tools associated with the machiningcenter, and will often have automatic workpiece handling as well.

To achieve the full six axes of motions in a present machining centerrequires that the movements of the table, column, spindle head, spindle,and bed be coordinated and that these sometimes massive components bemoved in very controllable finite increments. Because all of thesecomponents are being moved, many times simultaneously under computernumerical control, accuracy requires a rigidity to the components and anaccurate path through which the components can be moved. This hasresulted in the development of more rigid and massive components such asfor the bed and column and very expensive and finely formed ways alongwhich the components can travel relative to each other in the lineardirections.

Although the modern machining center provides very accurate machining,the machining center becomes very complex and expensive when it isdesigned to provide the maximum versatility of being able to machine anypoint on the exposed five surfaces of the typical cubic workpiece.

Modern machining centers are typically rigidly attached to a supportstructure such as a floor to prevent shifting of the machine toolcomponents and to maintain accuracy. However, the rigid attachmentcombined with the movement and working of the machine tool componentscan lead to deleterious vibration. This vibration detrimentally affectsthe ability of the machine tool to provide smooth surface finishes onthe object being machined and also limits the ability of the machinetool to rapidly accelerate the operator with respect to the object(.e.g, the spindle head with respect to the workpiece).

Attempts have been made to isolate machine tools from externalvibrations traveling through the floor by placing vibration damping padsbeneath the machine tools. However, these machine tools must still bebolted or otherwise solidly attached to the supporting floor whichlimits the damping ability. This approach also fails to mitigate thevibrations established by the moving components of the machine tool andthe interaction of the operator and the object.

Raising the natural frequency of a conventional machine tool caneliminate some of the detrimental vibrations that occur under normaloperating conditions. However, the necessary rigid attachment to asupport structure limits the machine tool designer's ability to raisethe machine tool's natural frequency. Additionally, most conventionalmachine tools have a structure that includes a massive base, to providerigidity and stability, and less massive moving components. Thisdifference in masses also limits the machine tool designer's ability toraise the machine's natural frequency and to lessen the undesirablevibrational effects.

It would be advantageous to design a machine tool having a base platformand a movable platform isolated from the supporting floor where theplatforms had more desirable mass ratios.

SUMMARY OF THE INVENTION

The present invention relates generally to a machine tool isolationsystem in which a machine tool cooperates with a vibration isolationcomponent. The isolation component is configured to be mounted between afloor or other support structure and the machine tool to raise thenatural frequency of the machine tool. The isolation system comprises abase platform configured to receive and hold a workpiece. The baseplatform may include a plurality of base legs extending downwardlytowards the floor.

A tool platform is configured to receive and hold a tool. An actuatormechanism, such as a plurality of extensible legs, is connected betweenthe base platform and the tool platform to selectively move the toolplatform with respect to the base platform. Furthermore, a vibrationisolation component is disposed between the base legs and the floor tohelp isolate the machine tool from its support structure. If the machinetool is designed without the plurality of base legs, the vibrationisolation component can be mounted between the base platform and thefloor.

According to additional aspects of the invention, the vibrationisolation component includes a spring and a damper. The spring anddamper can be combined in a single material, such as a composite rubberpad.

According to additional aspects of the invention, the base platform andthe tool platform are designed to have a ratio of masses ranging fromapproximately 0.5 to 2.0. Most preferably, the platforms are ofapproximately equal mass.

The invention also relates generally to a method for raising the naturalfrequency of a machine tool supported on a support structure and alsofor raising the possible relative acceleration of one machine toolplatform with respect to the other machine tool platform. The machinetool in this method is of the type configured to rigidly hold aworkpiece relative to one of the platforms and to hold a tool withrespect to the other platform. The platforms are connected by anactuator mechanism capable of moving the platforms with respect to eachother.

The method comprises the steps of forming a pair of platforms forsupporting the workpiece and the tool, respectively; sizing the pair ofplatforms so the ratio of platform masses is in the range from 0.5 to2.0; and separating the pair of platforms from the support structure bya vibration isolation component.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a view in elevation of a machine tool assembly for use withthe machine tool isolation system in accordance with the invention;

FIG. 2 is a top plan view of the machine tool of FIG. 1;

FIG. 3 is a view in perspective of a second embodiment of a machine toolassembly for use with the machine tool isolation system in accordancewith the present invention;

FIG. 4 is a view in elevation of the machine tool of FIG. 3;

FIG. 5 is a top view of the machine tool of FIGS. 3 and 4 as viewedthrough the section of the plane 5--5 of FIG. 4;

FIG. 6 is a view in elevation of a third embodiment of a machine toolassembly for use with the machine tool isolation system in accordancewith the invention;

FIG. 7 is a partial view in elevation of a leg and instrument armarrangement usable with any of the embodiments;

FIG. 8 is a schematic view of a control for a machine tool;

FIG. 9 is a schematic diagram of a second embodiment of a control;

FIG. 10 is a schematic diagram of a third embodiment of a control;

FIG. 11 is a view in perspective of a fourth embodiment of a machinetool assembly for use with the machine tool isolation system inaccordance with the invention;

FIG. 12 is a view in perspective of a fifth embodiment of a machine toolassembly for use with the machine tool isolation system in accordancewith the invention;

FIG. 13 is a view in perspective of a sixth embodiment of a machine toolassembly for use with the machine tool isolation system in accordancewith the invention;

FIG. 14 is a view in longitudinal section of a powered extensible legusable with the machine tools;

FIG. 15 is a partial view in longitudinal cross section, to an enlargedscale, of one of the yoke assemblies for connecting the powered leg to aplatform or support;

FIG. 16 is a view in longitudinal cross section through the yokeassembly of FIG. 15 and taken in the plane of the line 16--16 in FIG.14;

FIG. 17 is a view in perspective of the yoke assembly of FIGS. 15 and16;

FIG. 18 is a foreshortened view in longitudinal cross-section of aninstrument arm usable with the machine tools;

FIG. 19 is a view in section of one end of the instrument arm of FIG. 18and taken in the plane 19--19 in FIG. 18;

FIG. 20 is a schematic view of an instrument arm using a laserinterferometer for measuring distances;

FIG. 21 is a schematic representation of a prior art machine toolconnected rigidly to a support structure;

FIG. 22 is a schematic representation of a machine tool combined with avibration isolation device according to a preferred embodiment of theinvention;

FIG. 23 is a front elevational view of an alternate embodiment of themachine tool in which the platforms are constructed as space frames andmounted to a vibration isolation component;

FIG. 23a is a cross-sectional view of one exemplary embodiment forattaching a leg of the machine tool to a support.

FIG. 24 is a front elevational view of an alternate embodiment of themachine tool and vibration isolator illustrated in FIG. 23.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to FIGS. 1 and 2, the machine tool of the first embodiment hasa base 10 in the nature of a support or platform and a spindle supportor platform 11 spaced from the base 10. A spindle head 12 is mounted onthe spindle platform 11 and is adapted to receive a rotating cuttingtool 13. A spindle drive assembly indicated generally by the numeral 14is mounted on the spindle platform 11 and the drive includes a motor 15connected by a power train to the spindle head 12 in a usual manner. Thebase platform 10 carries a workpiece support 16 which in turn receives aworkpiece represented by the part 17.

The spaced platforms 10 and 11 are joined together by six powered andextensible legs 20-25. Each of the legs is pivotally mounted at itslower extremity to the base platform 10 by a ball and socket joint 26.Similarly, each of the upper ends of the legs 20-25 is pivotallyattached to the spindle platform 11 by a second ball and socket joint27.

The legs 20-25 may be formed of telescoping upper and lower parts 20aand 20b, for example. The telescoping parts may be the piston rod 20aand cylinder 20b of a hydraulic cylinder. The length of such legs can beadjusted by controlling the volume of hydraulic fluid in each end ofeach cylinder.

The position of the spindle support 11 relative to the base support 10and therefore the position of the cutting tool 13 relative to theworkpiece 17 can be adjusted by simultaneously manipulating the lengthof each of the six legs 20-25. Within an envelope of motion the cuttingtool 13 can be applied against all five exposed surfaces of a cubic typeworkpiece. The only constraints to the envelope of motion relative tothe five exposed surfaces are the spread of the joints 26 on the basesupport 10 and the spread of the second joints 27 on the spindle support11, the minimum and maximum length of the legs 20-25, the total range oflinear motion of each of the legs, and the need to avoid placing certainlegs in a common plane for purposes of stability. Within the envelope ofmotion, this construction allows the machining of contours in threedimensions as well as straight line point-to-point machining.

The simultaneous manipulation of the length of each of the legs 20-25can achieve motion in all six axes. That is, motion in a lineardirection along each of the three orthagonal axes and rotary motionabout each of those three axes.

In the embodiment of FIGS. 1 and 2, the six legs may be considered to bearranged in three pairs. That is, the legs 20 and 21 constitute a pair,the legs 22 and 23 constitute a second pair, and the legs 24 and 25constitute a third pair. It should be noted that the legs of each pairare arranged so that they are at an angle with respect to each other.The joints 26 of the pair of legs 20 and 21 are close to each other. Thejoints 27 of adjacent legs 20 and 25, for example, are also close toeach other. The effect is that the lower joints 26 generally define atriangle and the upper joints 27 also generally define a triangle. Thesetwo triangles and the six legs generally define edges of an octahedron.As shown in FIGS. 1 and 2, the area of the base platform 10circumscribed by the lower ball joints 26 and the area of the spindlesupport 11 circumscribed by the upper ball joints 27 are substantiallythe same. This is advantageous for several reasons. First, such anarrangement maximizes the structural stiffness of the machine. Secondly,the footprint of the machine is minimized for a particular cubic size ofworkpiece to be handled. Also, a greater envelope of surface area forthe workpiece can be accommodated before certain legs and supports arepositioned in a common plane thereby creating a potentially ambiguousposition.

Referring to FIGS. 3-5, the second embodiment includes a base support orplatform 30, a spindle support 31 which mounts a spindle head 32 adaptedto receive a cutting tool 33. The spindle head is rotated by a spindledrive 34. The base support 30 and spindle support 31 are connected bysix extensible legs 40-45. The legs are arranged in three pairs such asthe pair 40 and 41 and legs of each pair cross each other so that theyare again mounted at an angle with respect to each other. The legs 40-45are also formed of telescoping upper and lower elements 40a and 40b, forexample.

The legs 40-45 are joined to the base support 30 at a first point neartheir lower end by a joint indicated generally by the numeral 50. Thejoint 50 includes a clevis 51 mounted for rotation about the axis of ashaft 52 that projects from the base support 30. A typical trunnion 53engages the lower element 40b-45b of each leg and is rotatably mountedin a clevis 51. It will thus be seen that a joint 50 provides twodegrees of freedom of movement.

The upper telescoping portions 40a-45a of the legs are similarly joinedto the spindle support 31 at second points along the length of the legsby joints 54. The joints 54 likewise consist of a clevis 55 rotatablymounted on a shaft 56 extending downwardly form the underside of thespindle support 31 and a trunnion 57 which supports the upper legportions 40a et seq. in the clevis 55. As can be seen in FIG. 5 inparticular, the joints 50 and 54 and their attachments to the supports30 and 31 define the corners of a six-sided polygon in each of the twosupports. As is apparent from FIGS. 3-5, the area of the base support 30that is circumscribed by the connections of six lower joints 50 with thebase support 30 is substantially the same as the area of the spindlesupport 31 that is circumscribed by the connections of the six upperjoints 54 with the spindle support 31.

The shafts 52 and 56 of the joints 50 and 54 can be mounted in theirrespective supports to project in any direction. The ball joints of thefirst embodiment could also be used in this second embodiment, and thetrunnion joints of this second embodiment could be used in the first.

The base support 30 mounts a workpiece support 58 which holds aworkpiece exemplified by the part 59.

The legs 40-45 may also be formed as hydraulic cylinders with the pistonrod defining the upper end 40a et seq. and the cylinder portion formingthe lower ends 40b et seq. Because the piston rod can rotate within thecylinder, the two degrees of motion afforded at each of the joints 50and 54 are sufficient. If the upper and lower portions of the actuatorsforming the legs cannot be allowed to twist, and actuator other than ahydraulic cylinder is used to accomplish the extension, and a thirddegree of rotational motion will be required in one or the other of theupper and lower joints 50 and 54. In the leg of FIGS. 14-17, anadditional degree of motion is required in the joints or compensationmust be provided for the linear inaccuracy resulting from relativerotation of the telescoping parts introduced by slight angulardisplacement of the yoke assemblies relative to each other. Instead ofusing hydraulic cylinders as the actuators for the legs, any means forachieving linear motion can be used such as forming the upper portion ofeach leg as a lead screw and mounting a rotating nut in the lowerportion of the leg or vice versa. Alternatives are linear motors,recirculating ball screw drives, chair drives, and so forth.

In the third embodiment of FIG. 6, neither the tool nor the workpiece islocated within the envelope defined by the leg structure. The workpiece60 is mounted on a workpiece support 61 which in turn is mounted on abase 62 that is attached to an upright 63. The six legs 64-69 areconnected at one end to the upright 63 by trunnion joints 70 in a mannersimilar to that of the second embodiment. The opposite ends of the legs64-69 are connected by trunnion joints 71 to the spindle support 72. Thespindle support carries a spindle 73 adapted to mount a tool 74 and thespindle 73 is driven by a spindle drive 75. The tool 74 projects awayfrom the envelope defined by the legs 64-69. The third embodiment isotherwise the same as the first embodiment.

In the third embodiment, the workpiece support 61 may be mounted on wayssupported by the base 62 so that the workpiece support 61 with theworkpiece 60 may move relative to the tool 74. Even though the workpiece60 is not mounted on the upright 63, the workpiece location relative tothe upright support 63 can be fixed, or at least known, at any instantin time.

Other arrangements of spindle and workpiece can also be employed, suchas mounting the workpiece above the spindle or mounting an upright 63 asin the third embodiment of FIG. 6 on ways so that it can travel alongthe length of a workpiece.

The legs must be moved in a coordinated manner in order to position thesupports or platforms relative to each other. The coordinated movementis preferably accomplished by a computer control which provides aposition signal for each leg to achieve a desired position for thespindle platform relative to the base platform and therefore for thecutting tool relative to the workpiece. Suitable control schemes areillustrated in FIGS. 8 and 9. In FIG. 8, the leg in the form of ahydraulic cylinder such as the legs 20-25 are controlled by a servovalve 100 which controls the volume of hydraulic fluid in the cylinderon each side of the piston and therefore the position of the piston rodwithin the cylinder. A computer 101 produces an output position commandin the line 102. That position command is compared in a summing circuit103 with a feedback position signal in a line 104 leading from anexciter/demodulator 105 that receives the signal from a sensing head 106traveling along a magnetic scale 107. The sensing head 106 is coupled tothe piston rod 20a et seq. so that changes in position of the piston rodwill be reflected in changes in position of the sensing head 106 alongthe magnetic scale 107 which is at a known position, either fixed orvarying, with respect to the hydraulic cylinder 20b et seq. The summingcircuit 103 produces a position error signal in a line 108 which inputsto an integration network 109, the output of which is a velocity commandin a line 110. The velocity command is compared with a velocity feedbacksignal in a line 111 leading from the exciter/demodulator 105 and thetwo signals are fed to a summing circuit 112 which produces an outputsignal representative of a velocity error. This velocity error signal isfed to a compensation network 113 where phase shift compensation takesplace, and the resulting compensated signal is fed to an amplifier 114which in turn controls the servo valve 100.

A similar control loop leading from the computer would be provided foreach of the six legs 20-25 and the computer 101 would generate an outputposition command for the desired position of each of the six legs toachieve a particular finite position of the cutting tool relative to theworkpiece.

The control arrangement of FIG. 9 is similar to that of FIG. 8 but isshown in relation to a motor 120 rotating a lead screw and nutarrangement. An encoder or resolver 121 is connected to the motor 120 toprovide a position feedback signal through the exciter/demodulator 122,and that position signal is compared at a summing junction 123 with theposition command from the computer 61 to produce a position error signalfed to the integration network 124 which outputs a velocity commandcompared at a summing junction 125 with the velocity position signalfrom a tachometer 126 connected to the motor 120. A compensation network127 functions to produce an appropriate signal to an amplifier 128connected to the motor drive. Once again, there would be a similar loopfor each of the six legs of the machine.

The control schemes of FIGS. 8 and 9 employ closed loop control.However, by using a stepping motor it is not necessary to have a closedloop control. An example of a control system using a stepping motor isshown in FIG. 10.

Position signals can be provided by sensors that are directly connectedto each of the legs or to the actuators for the legs. However, a moreaccurate approach uses separate instrument arms. Such an arrangement isshown in FIG. 7.

In FIG. 7, a six legged machine tool of the embodiment shown in FIGS.3-6 has separate instrument arms 130 and 131 associated with respectivepowered legs 44 and 45, respectively. The instrument arms 130 and 131are each linearly extensible and are connected at their lower ends tothe base platform 30 by trunnion joints 132 and at their upper ends tothe spindle platform 31 by trunnion joints 133. The trunnion joints 132and 133 are the same in structure and operation as the joints 50 and 54used to connect power legs 44 and 45 to the platforms 30 and 31.

The instrument arms 130 and 131 are used solely for the purpose ofsensing the relative positions of the platforms. The instrument arms caninclude a sensing head traveling along a magnetic scale to provide thedesired feedback signal as to length and therefore as to position. Otherforms of instrument arms can also be used. The advantage in using theseparate instrument arms is that the load deflections that will occur inthe power legs and their joints will not be translated into errors inthe position of the cutting tool. The instrument arms being smaller andlighter and carrying no weight other than their own, are not subject tothe same forces and deflections to which the powered legs are subject.

Although the instrument arms 130 and 131 are shown mounted parallel withrespective power legs, it is not necessary for the instrument arms to beso mounted. Instrument arms are not required to be associated with anyparticular power leg. It is, however, necessary to have at least sixinstrument arms to provide an unambiguous set for signals for thepositions of the supports or platforms relative to each other.

In the fourth embodiment of FIG. 11, one of the platforms is elevatedand the second platform is suspended from the first platform on the sixlegs. Specifically, a support structure is formed from three uprightcolumns 140 jointed together by a triangular framework of members 41. Aspindle housing 142 is supported on the triangular framework of members141 with a spindle 143 pointing downwardly towards a workpiece platform144. The workpiece platform 144 is suspended on six extensible poweredlegs 145-150 which are arranged in pairs of crossing legs, similar tothe arrangement of the legs 40-45 in the second embodiment of FIGS. 3, 4and 5. The workpiece platform 144 may mount a pallet with a workpiece(now shown) in the usual manner. The legs 145-150 are pivotally joinedat their upper ends to the members 141 and at their lower ends to theworkpiece platform 144 in a manner similar to that of the secondembodiment.

One advantage of suspending a platform on the six legs is that in caseof a gross power failure which could cause the power legs to lose theirability to support a platform, the work platform 144 would move awayfrom the spindle. This would result in no damage to either the spindle,the tool, or the workpiece because there would be no collision betweenthe parts. In contrast, in an arrangement as shown in the first andsecond embodiments, a gross power failure in which the power legs losetheir ability to support a platform could result in the spindle crashingin to the workpiece or workpiece support.

Instead of the workpiece platform being suspended beneath the spindleplatform, the workpiece platform could be above a suspended spindleplatform. Then, chips would naturally fall away from the workpiece.

The fifth embodiment of FIG. 12 also suspends a workpiece platform froma support. In addition, it provides an instrument arm associated witheach of the six power legs and a spoke-like system of connects of theends of the powered legs and instrument arms to the platform andsupport.

Specifically, the fifth embodiment of FIG. 12 has three upright columns155 joined at their base by three I-beams 156 (two of the beams areshown foreshortened for clarity). The top of each column 155 carries abearing plate 157 on which a vibration isolation member such as a coilspring 158 rests. A spindle housing 159 has three radiating support arms160 in the form of I-beams. The outer ends of the support arms 160 eachmounts a bearing plate 161 which rest upon a respective isolation member158.

The spindle head 159 is mounted on top a ring platform 162 from whichtwo series of spokes 163 and 164 project. The spokes 163 and 164 are oftwo lengths that alternate around the ring platform 162 and the spokesmount the universal joints 165 that connect the upper ends of sixpowered legs 166 to the platform 162. The lower ends of the powered legs166 are connected to universal joints 167 mounted at the ends of spokes168 and 169 which project radially from a ring-like work platform 170.The spokes 163, 164 and 168, 169 are of different lengths to accommodatethe overlapping and crossing arrangement of the powered legs 166, whichis similar to that in the second and fourth embodiments.

A similar arrangement of rings and spokes is used to mount universaljoints at the ends of six instrument arms 171. That is, a second ringstructure 172 is disposed beneath the ring support 162 at the spindleend and about the spindle 173. A series of radially projecting spokes174 and 175 of two different lengths project from the ring 172. Thebottom workpiece platform 170 contains a second ring 176 from which twoseries of spokes 177 and 178 project to mount the universal joints atthe bottom ends of the instrument arms 171. The instrument arms 171 arearranged in pairs of crossing arms in the same manner as the poweredlegs 166.

The use of spokes emanating from the platform allows the powered legsand instrument arms to be removed from close proximity to the centralaxis of the spindle head and workpiece support with the result that itis easier to load a workpiece onto the workpiece platform. This isillustrated in FIG. 12 in which a phantom line identifies a cubicworkpiece which could be accepted by the machine tool and it may benoted that there is an opening through the powered legs 166 andinstrument arms 171 to accommodate the insertion and removal of aworkpiece of that size.

The ring structure 172 and the ring 176 can be structurally independentfrom the ring platform 162 and the work platform 170, the instrumentarms 171 can be structurally isolated from the deflections of theplatforms induced by the powered legs 166.

The sixth embodiment of FIG. 13 arranges three of the six legs in adifferent attitude than that of the prior embodiments. Specifically,three of the legs are mounted in or near a common plane that includesthe upper platform. As shown in FIG. 13, a base 180 of generallytriangular shape mounts triangular columns 181 at each of its corners.Three powered legs 182, 183 and 184 extend from universal jointsdisposed near the upper end of each of the columns 181. The other endsof the three legs 182, 183 and 184 are mounted in universal joints atthe corners of a triangular spindle platform 185 which mounts a spindlehead 186. The remaining three powered legs 187, 188 and 189 extend fromuniversal joints in the base 180 upward to the three corners of thetriangular spindle platform 185. A workpiece platform 190 rests on thebase 180 within the envelope of the three lower legs 187, 188 and 189.

The embodiment of FIG. 13 functions in the same manner as the otherembodiments and demonstrates that it is not necessary for the legs toextend between two planes, so long as the legs extend between the twoplatforms. The six legs in the embodiment of FIG. 13 extend from theworkpiece platform represented by the base 180 and its columns 181, andto the spindle platform 185.

FIGS. 14-17 illustrate a ball screw driven powered leg usable with themachines of the present invention. Generally, a rotatable ball screw rod195 is mounted with a stationary platform yoke assembly indicatedgenerally by the reference numeral 196. A nut tube 197 surrounds and isoperatively connected to the ball screw rod by a plurality ofrecirculating balls 197'. The nut tube 197 is connected to a movableplatform yoke assembly indicated generally by the numeral 198. The yokeassemblies 196 and 198 are connected to the stationary and movableplatforms of the machine tool, respectively. The ball screw rod 195 isrotated by a hydraulic or electric motor 199 mounted on a bracket 200connected to the stationary yoke assembly 196. The motor has an outputshaft 201 connected to the ball screw rod 195 by a toothed belt 202operating between pulleys connectively to the output shaft 201 and theball screw rod 195. The ball screw rod 195 is journaled in a pair ofthrust bearings 203 mounted in a cage associated with a motor fork 204that forms part of the stationary platform yoke assembly 196. A bellows205 is connected at one end to the nut tube 197 and at the other end toa tube 206 which, in turn, is connected to the motor fork 204.

As the ball screw rod 195 is rotated by the motor 199, the nut tube 197will move along the length of the rod 195 in a direction dependent uponthe direction of rotation of the rod 195. The effect will be to reduceor extend the distance between the yoke assemblies 196 and 198 therebyvarying the effective length of the leg.

Referring specifically to FIGS. 15-17, the movable platform yokeassembly 198 includes a U-shaped fork 210 which is connected to the nuttube 197 and which has a central opening 211 through which the screw rod195 passes. A protective tube 212 extends from the fork 210 along theoutside of the screw rod 195. The side arms 213 and 214 of the fork 210mount bearing holders 215 that hold the inner race of thrust bearings216 which are received in recesses in opposite side faces of a block217. The block 217 has a central opening 220 which is flared from themid-point of the opening towards the opposite ends of the block 217, asshown in FIG. 16. The remaining two side faces of the block 217 havebearing recesses 221 which receive thrust bearings 222 held in place bya bearing retainers 223. The bearing retainers 223 are mounted in spacedarms 224 of a second fork attached to the movable platform. By reason ofthe construction, the two forks are disposed at 90° from each other.

As will be appreciate, the yoke assembly 198 allows rotary motion aboutan axis through the bearings 222 and rotary motion about an axis throughthe bearings 216. The flared shape of the opening 220 accommodates thelatter rotary motion. The construction and operation of the fixedplatform yoke assembly 196 is the same as that described for the movableplatform yoke assembly 198.

Mounting the yoke assemblies at points along the length of the poweredleg, rather than at the ends, results in a significant increase in theratio of the maximum to minimum distance between the yoke assemblies asthe leg moves.

A first proximity switch 225 is mounted in the nut tube 197 near thecage for the balls. A second proximity switch 226 is mounted near theend of the protective tube 212. The proximity switches 225 and 226 areused to halt motion when the ball screw rod 195 reaches the limits ofits allowed motion. That is, when the end of the ball screw rod 195changes the state of the proximity switch 226, the power leg will havebeen shortened to its pre-established limit of travel. The conditionshowing FIG. 14 is near that short limit of travel. On the other hand,when the end of the ball screw 195 changes the state of the proximityswitch 225, the length of the powered leg will have been extended to itsmaximum desired limit. In both cases, the proximity switches 225 and 226affect the continued actuation of the motor 199.

One form of instrument arm usable with the machine tools of the presentinvention, is illustrated in FIGS. 18 and 19. One end of the instrumentarm is formed with a solid rod 230 which anchors one end of a first tube231. The other end of the tube 231 mounts a slide bearing 232 whichslides about the outer one of a pair of concentric stationary tubes 233and 234. The stationary tubes 233 and 234 are each anchored on a rod 235forming the opposite end of the instrument arm. An outer protective tube236 is also anchored to the second rod 235 and surrounds the first tube231. It can be seen therefore, that the first tube 231 can telescoperelative to the stationary tubes 233 and 234 and the protective tube236.

One end of a scale rod 238 is anchored in the solid rod end 230 of theinstrument arm. The opposite end of the scale rod 238 is attached to apiston 239 which slides within the inner stationary tube 234. A readhead 240 surrounds the scale rod and is attached to the free end of theinner and outer stationary tubes 233 and 234. The read head 240 istherefore stationary with respect to the fixed end 235 of the instrumentarm and the scale rod 238 can move longitudinally within the read head240 as the instrument arm is extended or contracted. The scale rod 238and reading head 240 are of known construction and operation. Generally,the read head will sense increments of motion along the scale rod as thetwo are moved relative to each other and will produce a signal whichwhen amplified is used in a known manner to indicate the relativeposition and changes in position of the two parts. A usable digitalpositioning measuring system of scale rod and read head may be thatbuilt by Sokki Electronics Corporation and identified as the JS7 seriesof digital positioning systems.

It is important in the operation of the read head and scale rod that thescale rod be kept taut. To that end, air pressure is introduced to actupon the piston 239 which mounts one end of the scale rod 238. The airunder pressure is introduced through a central bore 245 in the fixed end235 of the instrument arm and the air under pressure travels through thespace between the inner and outer tubes 233 and 234 and to and throughan opening 246 in the inner tube 234 adjacent is attachment to the readhead 240. This introduces pressurized air or the hollow interior of theinner tube 234 in which the piston 239 rides. An orifice passageway 247extends longitudinally through the read head 240 so that the spacebetween the solid rod 230 of the instrument arm and the read head 240 isconnected to the hollow interior a vacuum is not created in that spaceas the two ends of the instrument arm move relative to each other. Thespace between the inner and outer stationary tubes 233 and 234 is alsoused to accommodate wiring 248 connecting the read head to the exteriorof the instrument arm.

The instrument arm is preferably mounted in a manner similar to that ofthe powered legs using yoke assemblies. As with the powered legs, toincrease the ratio of the maximum to minimum distance between the yokeassemblies, the yoke assemblies are preferably mounted intermediate theends such as at the locations 249 and 250 identified in FIG. 18.

The movable end 230 of the instrument arm includes a transverse casting255 having an inlet 256 and an outlet 257 for air under pressure. Theinlet and outlet are connected to a central circular raceway 258 inwhich a ball bearing 259 is disposed. Air under pressure introduced intothe casting 255 will cause the ball bearing 259 to roll rapidly alongthe raceway 258. This will induce an eccentric motion to the end 230 ofthe instrument arm about the longitudinal axis of the arm. Thiseccentric motion is useful to insure that the telescoping elements ofthe instrument arm can slide smoothly with respect to each other. At thesame time, the vibratory motion induced by the spinning ball bearing 259is in a direction transverse to the direction of motion being measuredand therefore does not significantly affect that measurement.

FIG. 20 illustrates a form of instrument arm which uses a laserinterferometer. The instrument arm is formed of concentric inner andouter tubes 260 and 261, respectively, that slide past each other onbearings 262 which preferably are made of a polytetraflouride material.A bellows 263 connects the end of the outer tube 261 to the outside ofthe inner tube 260 so as to close off the volume within the tubes andprevent contamination through the bearings 262. A laser beam from alaser light source 264 enters the hollow interior of the instrument legthrough a window 265 and is reflected off a mirror 266 into aninterferometer 267 where it is divided into two components. Onecomponent exits the interferometer and travels inside of the tubes to aretro-reflector 268 which is mounted at the closed end of the outer tube261. Light is reflected back down the tubes towards the interferometer267. The two light beam components are recombined within theinterferometer 267 and the combined components interfere with eacheither constructively or destructively depending on their phase. A photodetector within the laser source 264 detects the fringes that resultfrom the interferences between the two components of the light beam asthe retro-reflector 268 moves relative to the interferometer. The phaseis dependent upon the distance between the interferometer 267 and theretroflector 268 and the fringes are therefore indicative of changes inlength of the instrument arm.

The number of light waves in transit between the interferometer 267 andthe retro-reflector 268 depends not only on the distance between the twobut also on the speed of light. The speed of light in air is dependentupon the atmospheric pressure, temperature and humidity. Pressure andtemperature have the largest effect and therefore they must be known ifthe distance between the interferometer and retro-reflector is to becalculated based on the number of fringes. The air within the interiorof the instrument arm is vented to a collapsible bladder 270. As theinstrument arm expands, it displaces air that is stored within thebladder 270. The bladder 270 is limp at all times so that the pressurewithin the arm is equal to the ambient pressure outside of the arm. Asingle pressure transducer can then be used for all of the instrumentarms to determine the pressure of the air through which the light beamis passing.

A temperature measurement transducer 271 senses the internal temperaturein each instrument arm since the temperature may be localized. Theeffect of humidity is negligible and is ignored.

Instead of an instrument arm that has a structural integrity, it ispossible to use known forms of position transducers to measure thedistance between the platforms. An example of a usable positiontransducer is the cable actuated displacement transducers available fromHouston Scientific International, Inc. and identified as the 1850Series. In using such a transducer, a cable would be connected to one ofthe platforms and the transducer housing to the other platform. Apotentiometer within the housing would provide a signal indicative ofthe length of cable extending from the housing at any particularposition of the machine tool components.

A combination of measurements using the power legs and instruments armscan also be used to speed up positioning of the components of themachines. For example, the powered legs could be provided with a linearscale (such as in FIG. 8) or a rotary resolver or shaft encoder (such asin FIG. 9) to provide a position feedback signal that allows a grosspositioning of the platforms relative to each other. An associatedinstrument arm could then be used for fine positioning with the poweredlegs being moved at a slower rate to the final desired position.

The angles that the powered legs make with the platforms will effect thestiffness of the machine and the accuracy of the positioning of the toolrelative to the workpiece. The optimum position of the legs relative tothe platforms for achieving optimum vertical and horizontal stiffnesswould be about 35°. This assumes that each platform exhibits stiffnessalong its orthagonal axes. For achieving the best vertical andhorizontal resolutions to achieve accuracy, at nominal positions theoptimum angle of the legs relative to the platforms is about 41°.

The typical part program for a machine tool is designed to provideblocks of instruction concerning the X,Y,Z,A,B,C coordinates of the tooltip and workpiece relative to each other. Because the six legs of amachine tool in accordance with the present invention do not alignthemselves with the normal orthagonal coordinates, a method must bedeveloped to relate the normal coordinate block instructions to thelength of the six legs. The following method has been developed for thatpurpose. The steps are arranged in logic sequence form and can besummarized as follows:

I. Initializing present machine X,Y,Z,A,B,C coordinates

II. For each of six legs:

A. Initialize top and bottom pivot vector coordinates.

B. Calculate and initialize present leg length.

C. Define X,Y,Z,A,B,C home position for present leg length.

III. Set sub-block time (typically 0.02 seconds) sufficiently short toachieve desired linearity and precision of movement.

IV. For each part program:

A. For each block:

1. From the part program read machine coordinates of destination;X,Y,Z,A,B,C and feed rate

2. Using feed rate and sub-block time, compute the number of sub-blocksrequired to reach block destination.

3. For each sub-block:

(a) For each of six coordinates:

1. Present value=ending value of previous sub-block.

2. Ending value=(destination value minus present value) divided bynumber of sub-blocks remaining plus present value.

(b) Using the ending value of the six coordinates, compose a sub-blockending vector

(c) For each leg:

1. Rotate the top pivot vector to the ending angles for the currentsub-block.

2. Add a sub-block ending vector to the result.

3. Subtract the bottom pivot vector from the result.

4. Calculate the ending leg length by extracting the square root of thesum of the squares of the coordinates of the result of step (c)3.

5. Convert the ending leg length to the nearest integral servo positioncommand count.

6. Send the position count to a servo command buffer.

7. Calculate the leg velocity required to reach new leg length in onesub-block time.

8. Convert the leg velocity to the nearest integral servo command count.

9. Send velocity count to the servo command buffer.

(d) Send sub-block start command simultaneously to all leg servos.

B. A block is completed when no sub-blocks remain.

V. The task is completed when no blocks remain in the part program.

Initializing the present machine is a process which is known in themachine tool art as gridding. It establishes a home position in whichthe tip of the tool and the center of the workpiece cube are coincident.

As illustrated in FIG. 12, the use of a vibration isolation assembly,such as cable coil spring 158, can be helpful in isolating the machinetool from its surrounding support structure such as a floor or thecolumns 155 illustrated in FIG. 12. The support structure is ultimatelyattached to the earth which, in combination, has as extremely large massrelative to the machine tool. The isolation of the machine tool fromrigid contact with the support structure in other words, the decouplingof the machine tool from the mass of the support structure and the earthraises the natural frequency of the actuator mechanism acting betweenthe machine tool platforms and helps reduce the harmful effects ofvibration. It is also helpful to combine a damper with the spring in thevibration isolation assembly to damp the amplitude of vibrationsinitiated by movement of the machine tool platforms and interaction ofthe operator and object. This will permit cutting of a finer, moreprecise surface on the workpiece.

Additionally, the vibration isolation assembly permits higher relativeacceleration between the platforms, and specifically between the tooland the workpiece, so finer details may be machined in the workpiecewithout compromising adherence to the pre-programmed path and feed rate.For example, the vibration isolation component facilities contouring agiven radius of curvature at a higher feed rate with the same amount offorce moving the platforms.

A machine tool 298 affixed to its support structure and alternatively amachine tool cooperating with a vibration isolation component 308 isrepresented schematically and described in greater detail with referenceto FIGS. 21-22, respectively. As illustrated in FIG. 21, a base platform300 is rigidly connected to a support structure, such as a floor 302, asis done with conventional machine tools. Base platform 300 is connectedto an upper platform 304 by an actuator mechanism 306 that is capable ofmoving platform 304 in a plurality of directions with respect toplatform 300. Actuator mechanism 306 may include the six extensible legsdescribed above in various embodiments but is represented schematicallyas a spring because any mechanical actuator mechanism has springcharacteristics. It should be noted that although the platforms arereferred to as a base platform and an upper platform for descriptivepurposes, the platforms could be arranged in orientations other than oneabove the other.

In the schematic representation of FIGS. 21 and 22, the vibrationalanalysis is calculated with respect to only one axis lying along thespring. It should be realized that in actual application, e.g. when theplatforms are connected by the six extenible legs, the vibrationaleffects may occur along six different axes and a similar analysis can beconducted for each axis.

In the schematic representation, moveable platform 304 has a massrepresented by M₁ but base platform 300 is affixed to its supportstructure so it is reasonable to assume its mass is M₁ plus the mass ofthe object to which it is rigidly attached. Because the supportstructure is mounted on a foundation that is ultimately indirectly ordirectly coupled to the earth, a good approximation of this total massis an infinite mass. Also, actuator mechanism 306 has inherentspring-like characteristics and its stiffness is represented by springconstant K₁. Thus, the natural frequency acting between platforms 300and 304 and affecting actuator mechanism 306 can be described by theequation: ##EQU1##

However, if base platform 300, having a mass approximately equal to M₁,is mounted to a vibration isolation device 308, such as thatschematically illustrated in FIG. 22, the natural frequency actingbetween the platforms is increased by approximately the square root of2. Vibration isolation device 308 effectively decouples base platform300 from the mass of the earth permitting an increase in the naturalfrequency of actuator mechanism 306 between platforms 300 and 304. Thisincreased natural frequency has a natural damping effect, but vibrationisolation device 308 preferably further damps the amplitude of vibrationoscillations established between platforms 300 and 304.

By isolating or decoupling the platforms from their supporting structureand by using platforms of approximately equal mass, the springcharacteristics of the actuator mechanism 306 effectively acts as thoughthe single spring illustrated in FIG. 21 is actually two springs ofequal length, each spring having a spring constant of 2K₁ (see FIG. 22).Because each spring can be considered separately, the natural frequencyis calculated as raised by a factor equal to the square root of 2. Thismaximum natural frequency acting between platforms 300 and 304 can beexpressed by the equation: ##EQU2## If the platform masses are notequal, the increase in the natural frequency is less, but it may stillbe sufficient for many applications. As the disparity in platform massesincreases, the corresponding increase in natural frequency is reduced.Accordingly, the ratio of platform masses is preferably approximately0.5 to 2.0, more preferably approximately 0.75 to 1.25, and mostpreferably approximately 0.9 to 1.1.

Preferably, vibration isolation assembly 308 includes a spring 310 and adamper 312. Damper 312 can be connected between base platform 300 andmovable platform 304, but this arrangement tends to inhibit the movementof platform 304 with respect to platform 300. Therefore, preferably bothspring 310 and damper 312 are mounted between the base platform 300 andsupport structure 302.

If vibration isolation device 308 includes only spring 310, the naturalfrequency of machine tool 298 is increased, but detrimental relativevibration of platforms 300 and 304 may remain because actuator mechanism306 has characteristics similar to an undamped spring. Thus, theaddition of damper 312 is preferred to reduce this relative vibration.

Spring 310 and damper 312 may be combined in a single material, such asa resilient pad having spring and damping characteristics. Examples ofresilient pads that can be used to help isolate the machine tool fromits supporting structure include pads made from a variety of rubbers,plastics and composite materials. Plastic or rubber reinforced withfiberglass or felt fibers are effective. One preferred material is apolymer having high damping characteristics and sold by EAR SpecialityComposites Corporation of Indianapolis, Ind. under Spec. No. C-1002-99.This material preferably has a durometer rating of approximately 56measured on the Shore A Scale. A similar material is supplied bySorbothone, Inc. of Kent, Ohio. Another pad material having spring anddamping characteristics is cable, such as steel cable, that is coiledlike a helical spring and laid on its side between the machine tool andits support structure. (See FIG. 12) Of course, the coils of cable mustbe held in place by rigid supports attached thereto, and the diameter ofthe cable must be sized according to the weight and actuating forcesexerted by the machine tool. These matters are well within the ken ofthe artisan, guided by the principles set forth herein.

Vibration isolation component 308 also helps isolate the machine toolfrom environmental vibrations. For example, the movement of trains ortrucks in proximity to working machine tools can induce vibrations inthe floor capable of affecting the precision machining of workpieces.Vibration isolation component 308 substantially dissipates thoseenvironmental influences.

Additionally, vibration isolation component 308 permits greateracceleration of one platform with respect to the other. The accelerationof each platform equals the force exerted by actuator mechanism 306against that platform divided by the mass of the platform, i.e. platformacceleration=force_(actuator) /mass_(platform). The maximum relativeacceleration of one platform relative to the other is determined bycalculating and summing the maximum acceleration for each platform.

In the conventional machine tool illustrated in FIG. 21, bottom platform300 is affixed to floor 302 which, in turn, is ultimately coupled to theearth, and thus its mass is assumed to be an infinite mass. Therefore,the relative acceleration of platform 304 with respect to platform 300can be calculated as follows: ##EQU3##

In the inventive embodiment illustrated in FIG. 22, base platform 300 isnot fixed to floor 302, but rather is loosely mounted on vibrationisolation component 308 to permit movement of platform 300 in responseto the force exerted by actuator mechanism 306. Thus, the relativeacceleration of the platforms can be estimated as follows: ##EQU4## Inother words, by isolating the machine tool via vibration isolationcomponent 308, the relative acceleration of two platforms ofapproximately equal mass is double the relative acceleration obtainablewhen one of the platforms is rigidly attached to a support structure,effectively providing it with an infinite mass.

Even in actual applications, a machine tool having platforms ofapproximately equal mass mounted on a vibration isolation component 308can nearly double the relative acceleration of the platforms compared toa machine tool in which the base platform is rigidly attached to thesupport structure. For example, a machine tool having a milling cutterattached to one platform can cut around a smaller radius of curvature atthe same feed rate when provided with a vibration isolation component308. This assumes that component 308 isolates the machine tool platformsfrom rigid attachment to the external support structure and also assumesa given amount of force is provided by actuator mechanism 306 in bothsituations. Although mounting the machine tool on a pad, such as arubber pad, does not allow platform 300 complete freedom of movement asit would have if it were floating in space, there is still a substantialincrease in relative acceleration between the platforms whichdramatically facilitates more rapid changes in cutter direction.

In an actual application, vibrations would occur along more axes thanthe single axis illustrated in FIGS. 21 and 22. Depending on the type ofmachine tool, vibrations could be established along six different axes,commonly referred to as X,Y,Z,A,B, and C axes and resulting from linearand torsional forces exerted during movement of the platforms withrespect to each other. As a result, it is often desirable to divide thevibration isolation assembly into sections or components that are spacedfrom one another to absorb vibrations resulting from both linear andtorsional forces. For example, the resilient pad can be separated intothree sections disposed at separate outlying areas between base platform300 and its support structure. However, those resilient pads must beable to incur both compressive and shear forces. Therefore, it may bedesirable to use additional resilient pads disposed at appropriateangles to absorb the vibrational forces substantially in compression asdescribed below with respect to FIG. 24.

A practical example of a machine tool cooperating with a vibrationisolation component is illustrated in FIG. 23. Further description ofthis machine tool can be obtained from U.S. patent application, Ser. No.08/261,682 filed on Jun. 17, 1994 which is hereby incorporated byreference and relied on. A machine tool 320 includes a lower or baseplatform 322 connected to an upper platform 324 by an actuator mechanism326. Actuator mechanism 326 preferably includes a plurality ofextensible legs 328 such as the extensible legs described with referenceto FIGS. 14-17.

In the illustrated embodiment, base platform 322 includes a base 330,preferably having a plurality of legs 332. Although various numbers oflegs can be used, it is desirable to use three legs configured to reston a support structure such as a floor 334. Base platform 322 alsoincludes an object holder 336 configured to hold an object such as aworkpiece 338.

Upper platform 324 includes a tool holder 340 configured to hold a tool342. Tool 342 interacts with workpiece 338 when upper platform 324 ismoved along a pre-programmed path relative to base platform 322 byactuator mechanism 326.

In this embodiment, both platforms 322 and 324 are each formed as aspace frame having a plurality of interconnected struts 344. Theconstruction of space frames using struts 344 renders rigid yetrelatively lightweight platforms 322 and 324.

Vibration isolation component 308 is attached to the bottom of base 330which, in this embodiment, is at the bottom of legs 332. The particularvibration isolation device illustrated includes a pair of resilient pads346 disposed between each leg 332 and floor 334. Preferably, pads 346are disposed on either side of a portion 347 of legs 332 and legs 332are held by a bolt 349 which maintains pads 346 in slight compression(see FIG. 23a). Also, resilient pads 346 include a material such asthose described above having both spring characteristics and dampingcharacteristics. However, vibration isolation device 308 can comprisesprings without dampers, combinations of separate springs and dampers,or other materials having appropriate spring rate and dampingcharacteristics. Additionally, vibration isolation device 308 is notlimited to use with this particular embodiment, but can also be usedwith other machines and machine tools such as those illustrated anddescribed above. For example, a resilient pad 348 may be disposedbetween base 10 of the machine tool illustrated in FIG. 1 and a floor350.

It should also be noted that machine tool 320 may optionally include aplurality of counterbalances 352 to counter intertial effects.Counterbalances 352 are preferably gas springs connected between baseplatform 322 and upper platform 324.

The mass ratio of base platform 322 to upper platform 324 is preferablyin the range from approximately 0.5 to 2.0. However, it is oftendesirable for the mass of base platform 322 to be as close as possibleto the mass of upper platform 324 to optimize the natural frequency ofthe system.

Alternatively, machine tool 320 may be mounted on a vibration isolationdevice 308 as illustrated in FIG. 24. As illustrated, vibration isolator308 includes a plurality of damping components, such resilient pads 354,preferably arranged at outlying regions of base 330. Pads 354 arearranged at angles with respect floor 334 to isolate machine tool 320from floor 334 while absorbing or damping the vibrational effectspotentially produced along six different axes. The pads 354 are orientedto absorb, substantially in compression, the vibration exerted along anyof the six axes. Thus, the pads need only damp the vibrations incompression rather than in shear. This makes it easier to select dampingmaterials because only knowledge of the linear or compressivecharacteristics of the material is necessary to design the overallisolation system. The appropriate angles and orientations of the pads354 depend on the design of the particular machine tool and can bedetermined by the artisan of ordinary skill in the art relying on theteachings herein.

Although the invention has been described in relation to machine tools,it is also the usable in connection with any machine that requires thatan operator be brought into position with respect to an object. It isalso useful for a wide variety of tools other than the traditionalcutting tool.

I claim:
 1. A machine tool isolation system in which a machine toolassembly cooperates with a vibration isolation assembly, the machinetool assembly including a base platform having a plurality of base legs,the base platform being configured to receive and hold a workpiece; atool platform configured to receive and hold a tool; and a plurality ofextensible legs connected between the base platform and the toolplatform to move the tool platform with respect to the base platform,the vibration isolation assembly being configured to be mounted betweena supporting floor and the machine tool assembly to raise the naturalfrequency acting between the base platform and the tool platform,comprising:vibration isolation means, disposed between the base legs andthe floor, for decoupling the base platform from the supporting floor.2. The machine tool isolation system as recited in claim 1, wherein thevibration isolation means includes a spring and a damper.
 3. The machinetool isolation system as recited in claim 1, wherein the vibrationisolation means includes a resilient pad.
 4. The machine tool isolationsystem as recited in claim 1, wherein the vibration isolation meanscomprises a plurality of resilient pads, one pad being disposed betweeneach leg and the floor.
 5. The machine tool isolation system as recitedin claim 3, wherein the resilient pad has combined springcharacteristics and damping characteristics.
 6. The machine toolisolation system as recited in claim 5, wherein the resilient pad has adurometer rating in the range from 52 to
 60. 7. The machine toolisolation system as recited in claim 4, wherein there are three baselegs and three resilient pads.
 8. The machine tool isolation system asrecited in claim 3, wherein the base platform and the tool platform havea ratio of masses ranging from approximately 0.5 to 2.0.
 9. The machinetool isolation system as recited in claim 8, wherein the ratio of massesranges from approximately 0.75 to 1.25.
 10. The machine tool isolationsystem as recited in claim 9, wherein the tool platform hasapproximately the same mass as the base platform.
 11. A vibrationisolation system including a machine cooperating with a vibrationisolator configured to isolate the machine from its support structureand to thereby raise the natural frequency within the machine,comprising:a base machine component configured to hold an object; anoperator machine component configured to hold an operator forinteraction with the object, wherein the ratio of the mass of theoperator machine component to the mass of the base machine component isin the range from approximately 0.5 to 2.0; an actuator mechanismconnected between the base machine component and the operator machinecomponent to move the operator machine component with respect to thebase machine component; and a vibration isolator connected between themachine and its support structure to raise the natural frequency of theactuator mechanism acting between the base machine component and theoperator machine component by a factor of at least 1.20.
 12. Thevibration isolation system as recited in claim 11, wherein the vibrationisolator includes a material having spring characteristics effective todecouple the machine from its support structure.
 13. The vibrationisolation system as recited in claim 11, wherein the vibration isolatorincludes a spring and a damper.
 14. The vibration isolation system asrecited in claim 12, wherein the vibration isolator comprises aresilient pad disposed between the base machine component and thesupport structure.
 15. The vibration isolation system as recited inclaim 14, wherein the resilient pad is a polymer pad having dampingcharacteristics sufficient to reduce the amplitude of vibrationsestablished between the base and operator machine components.
 16. Avibration isolation system including a machine cooperating with avibration isolator configured to isolate the machine from its supportstructure and to thereby raise the natural frequency within the machine,comprising:a base machine component configured to hold an object, anoperator machine component configured to hold an operator forinteraction with the object, wherein the ratio of the mass of theoperator machine component to the mass of the base machine component isin the range from approximately 0.5 to 2.0; an actuator mechanismconnected between the base machine component and the operator machinecomponent to move the operator machine component with respect to thebase machine component; a vibration isolator connected between themachine and its support structure to raise the natural frequency of theactuator mechanism acting between the base machine component and theoperator machine component by a factor of at least 1.20; the vibrationisolator including a material having spring characteristics effective todecouple the machine from its support structure, the material comprisinga resilient pad disposed between the base machine component and thesupport structure the resilient pad being a polymer pad having dampingcharacteristics sufficient to reduce the amplitude of vibrationsestablished between the base and operator machine components; whereinthe base machine component includes a plurality of legs and the polymerpad is split into sections, further wherein at least two sections aredisposed between each leg and the support structure, the sections beingoriented at an angle to receive vibrational forces substantially incompression.
 17. The vibration isolation system as recited in claim 14,wherein the ratio of the mass of the operator machine component to themass of the base machine component is in the range from approximately0.9 to 1.1.
 18. The vibration isolation system as recited in claim 14,wherein the actuator mechanism includes at least six extensible legs.19. A method for raising the natural frequency of a machine toolsupported on a support structure and for raising the maximum relativeacceleration of one machine tool platform with respect to the othermachine tool platform, the machine tool being configured to rigidly holda workpiece relative to one of the platforms and to hold a tool withrespect to the other platform, the platforms being connected by anactuator mechanism capable of moving the platforms with respect to eachother, comprising the steps of:forming a pair of platforms forsupporting the workpiece and the tool, respectively; establishing themass of each platform so the ratio of the mass of one platform to themass of the other is in the range from 0.5 to 2.0; and separating thepair of platforms from the support structure by a vibration isolationdevice.
 20. The method of claim 19 for raising the natural frequency ofa machine tool and for raising the maximum relative acceleration of onemachine tool platform with respect to the other, wherein the step ofseparating includes the steps of:connecting the pair of platforms to thefloor by a material having spring characteristics; and connecting thepair of platforms to the floor by a material having dampingcharacteristics.
 21. The method of claim 20 for raising the naturalfrequency of a machine tool and for raising the maximum acceleration ofone machine tool platform with respect to the other, further comprisingthe step of combining the spring material and the damping material intoa single material.